US20210199381A1 - Cooling tower speed reducer - Google Patents
Cooling tower speed reducer Download PDFInfo
- Publication number
- US20210199381A1 US20210199381A1 US17/132,729 US202017132729A US2021199381A1 US 20210199381 A1 US20210199381 A1 US 20210199381A1 US 202017132729 A US202017132729 A US 202017132729A US 2021199381 A1 US2021199381 A1 US 2021199381A1
- Authority
- US
- United States
- Prior art keywords
- speed reducer
- casing
- shaft
- cooling tower
- main body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 238000001816 cooling Methods 0.000 title claims abstract description 53
- 239000003638 chemical reducing agent Substances 0.000 title claims abstract description 50
- 239000000314 lubricant Substances 0.000 claims description 7
- 230000002093 peripheral effect Effects 0.000 description 8
- 238000007789 sealing Methods 0.000 description 5
- 239000003921 oil Substances 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 239000000498 cooling water Substances 0.000 description 3
- 238000003780 insertion Methods 0.000 description 3
- 230000037431 insertion Effects 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000009423 ventilation Methods 0.000 description 2
- 229910001018 Cast iron Inorganic materials 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 239000010779 crude oil Substances 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000945 filler Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000007670 refining Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
- F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
- F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
- F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H1/222—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with non-parallel axes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/029—Gearboxes; Mounting gearing therein characterised by means for sealing the gearboxes, e.g. to improve airtightness
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/038—Gearboxes for accommodating bevel gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/039—Gearboxes for accommodating worm gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0415—Air cooling or ventilation; Heat exchangers; Thermal insulations
- F16H57/0416—Air cooling or ventilation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0493—Gearings with spur or bevel gears
- F16H57/0495—Gearings with spur or bevel gears with fixed gear ratio
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0498—Worm gearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
- F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
- F16J15/3236—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips with at least one lip for each surface, e.g. U-cup packings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
- F28C1/00—Direct-contact trickle coolers, e.g. cooling towers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F25/00—Component parts of trickle coolers
Definitions
- Certain embodiments of the present invention relate to a cooling tower speed reducer.
- a cooling tower speed reducer which drives a cooling fan of a cooling tower.
- a problem may arise in sealing performance between an externally exposed shaft (for example, an output shaft) and a casing in some cases.
- an externally exposed shaft for example, an output shaft
- the speed reducer is exposed to a high humidity atmosphere. Consequently, it is necessary to satisfactorily maintain the sealing performance between the shaft and the casing so that not only dust but also moisture does not enter an inside of the speed reducer.
- a cooling tower speed reducer that reduces a speed of rotation input from an input shaft to rotationally drive a cooling fan installed inside a cooling tower.
- the cooling tower speed reducer includes a seal member disposed between a shaft and a casing.
- the seal member includes a first member externally fitted to the shaft and a second member internally fitted to the casing.
- the first member includes a first member main body and a first lip portion provided on an outer periphery of the first member main body.
- the second member includes a second member main body with which the first lip portion comes into contact, and second lip portions provided on an inner periphery of the second member main body to come into contact with the first member main body.
- FIG. 1 is a sectional view illustrating a cooling tower to which a cooling tower speed reducer according to an embodiment of the present invention is applied.
- FIG. 2A is a perspective view when the cooling tower speed reducer according to the embodiment is viewed from an obliquely upper front side
- FIG. 2B is a perspective view when the cooling tower speed reducer is viewed from an obliquely lower front side.
- FIG. 3A is a side view of the cooling tower speed reducer according to the embodiment
- FIG. 3B is a perspective view when the cooling tower speed reducer is viewed from an obliquely lower rear side.
- FIG. 4 is a side sectional view of the cooling tower speed reducer according to the embodiment.
- FIG. 5 is an enlarged view of a section A in FIG. 4 .
- FIG. 6 is a view illustrating a seal structure between a shaft and a casing in the related art.
- a gap between a casing and a shaft is sealed with an oil seal, and a slinger member is provided in the shaft so that a gap between a seal portion and the slinger member is filled with a lubricant.
- a speed reducer prevents oil from leaking out of the speed reducer or prevents external moisture from entering the speed reducer.
- it is necessary to provide the slinger member. Consequently, the number of components increases, and the speed reducer has a complicated configuration.
- FIG. 1 is a sectional view illustrating a cooling tower 100 to which a cooling tower speed reducer 1 according to an embodiment of the present invention is applied.
- the cooling tower speed reducer (hereinafter, simply referred to as a “speed reducer”) 1 according to the present embodiment is applied to the cooling tower 100 .
- the cooling tower 100 cools cooling water used in a cryocooler for air conditioning or a process fluid for refining crude oil.
- warmed cooling water W 1 introduced into a tower unit 110 is sprayed onto a surface of a filler 130 by a sprinkler 120 , and external air A 1 fetched by a cooling fan 140 is blown to dropping water W 2 .
- the water W 2 is partially evaporated, the remaining water is cooled, and cooling water W 3 collected in a bottom portion of the tower unit 110 is circulated to an air conditioner by a pump.
- the cooling fan 140 is provided in an upper portion of the tower unit 110 , and discharges moisture evaporated in the tower unit 110 to external air above.
- the cooling fan 140 is connected to a motor 150 via the speed reducer 1 .
- the speed reducer 1 reduces a speed of power of the motor 150 , and outputs the power to rotationally drive the cooling fan 140 .
- the speed reducer 1 of the present embodiment can be used for any type of the cooling towers (for driving the cooling fan).
- the speed reducer 1 can also be used for an air-cooled heat exchanger (air fin cooler) having a closed type, a suction ventilation type, or a force ventilation type.
- FIGS. 2A and 2B are perspective views when the speed reducer 1 is viewed from an obliquely upper front side and an obliquely lower front side.
- FIGS. 3A and 3B are side views of the speed reducer 1 , and are perspective views when the speed reducer 1 is viewed from an obliquely lower rear side.
- FIG. 4 is a side sectional view of the speed reducer 1 .
- the speed reducer 1 includes an input shaft 20 , an intermediate shaft 30 , and an output shaft 40 which are sequentially connected to transmit power, and a casing 50 that accommodates the shafts.
- the input shaft 20 is disposed so that an axial direction is oriented in a substantially horizontal direction, and the intermediate shaft 30 and the output shaft 40 are disposed so that the respective axial directions are oriented in an upward-downward direction substantially perpendicular to the input shaft 20 .
- the input shaft 20 , the intermediate shaft 30 , and the output shaft 40 are pivotally supported by bearings 21 , 31 , and 41 disposed between the respective shafts and the casing 50 .
- the respective axes of the input shaft 20 , the intermediate shaft 30 , and the output shaft 40 are located in the mutually same plane.
- directions of the speed reducer 1 will be defined as follows.
- a direction along the input shaft 20 (rightward-leftward direction on a paper surface in FIG. 4 ) will be set as a “forward-rearward direction”
- a vertical direction perpendicular to the forward-rearward direction on the paper surface in FIG. 4 will be set as the “rightward-leftward direction”
- a direction along the output shaft 40 (upward-downward direction on the paper surface in FIG. 4 ) will be set as the “upward-downward direction”.
- a side where the input shaft 20 is exposed from the casing 50 will be set as a “front side”
- a side opposite thereto will be set as a “rear side”.
- a bevel pinion 22 is formed in a rear side tip of the input shaft 20 .
- the bevel pinion 22 meshes with a bevel gear 32 connected to the intermediate shaft 30 to be integrally rotated.
- An intermediate gear 33 is formed on an outer peripheral surface of the intermediate shaft 30 .
- the intermediate gear 33 meshes with an output gear 42 connected to the output shaft 40 to be integrally rotated.
- a front side tip of the input shaft 20 is exposed from the casing 50 , and a motor 150 (refer to FIG. 1 ) is connected to the tip to receive input power (rotating motion).
- An upper end of the output shaft 40 is exposed from the casing 50 , and is connected to the cooling fan 140 (refer to FIG. 1 ).
- a rotating motion input to the input shaft 20 is transmitted to the output shaft 40 while a speed of the rotational motion is reduced via a gear set of the bevel pinion 22 and the bevel gear 32 and a gear set of the intermediate gear 33 and the output gear 42 , and is output from the output shaft 40 to the cooling fan 140 .
- the bevel pinion 22 , the bevel gear 32 , the intermediate shaft 30 , the intermediate gear 33 , and the output gear 42 form a reduction mechanism that reduces a speed of rotation of the input shaft 20 and transmits the rotation to the output shaft 40 .
- the gear set of the bevel pinion 22 and the bevel gear 32 may be a gear set of a hypoid gear or a worm gear.
- a fan (impeller) 23 is disposed in a tip of a front side portion exposed (protruded) from the casing 50 in the input shaft 20 (omitted in the illustration in FIG. 4 ).
- the fan 23 rotates in association with the rotation of the input shaft 20 , and blows wind toward the casing 50 located behind.
- the casing 50 is an integral cast component (made of cast iron) formed in a substantially rectangular parallelepiped shape that is slightly long in the forward-rearward direction.
- the casing 50 has a front surface 51 , a rear surface 52 , an upper surface 53 , a lower surface 54 , and both right and left side surfaces 55 and 55 .
- a circular through-hole 51 a is formed on the front surface 51 of the casing 50 .
- a shaft support member 56 that pivotally supports the input shaft 20 via a bearing 21 is attached to the through-hole 51 a .
- the shaft support member 56 is formed in a substantially cylindrical shape along the forward-rearward direction, and is fixed to the casing 50 in a state where a rear half portion is inserted into the casing 50 from the through-hole 51 a .
- a front end of the shaft support member 56 has a seal member 25 that seals a gap formed with the input shaft 20 .
- a through-hole 52 a is formed on the rear surface 52 of the casing 50 .
- the through-hole 52 a has a wide shape in the rightward-leftward direction, and is formed to have a size through which a gear member of the bevel gear 32 and the output gear 42 can pass.
- the through-hole 52 a is a hole portion for incorporating the bevel gear 32 and the output gear 42 into the casing 50 when assembled. When assembled, the intermediate gear 33 and the output gear 42 are inserted into the casing 50 from the through-hole 52 a , and are attached to the intermediate shaft 30 and the output shaft 40 inside the casing 50 .
- the through-hole 52 a is closed by a cover member 521 .
- First bearing holes 53 a and 54 a for supporting the intermediate shaft 30 and second bearing holes 53 b and 54 b for supporting the output shaft 40 are formed on the upper surface 53 and the lower surface 54 of the casing 50 .
- the first bearing holes 53 a and 54 a are coaxially formed to have substantially the same inner diameter, and each of bearings 31 is internally fitted thereto so that the intermediate shaft 30 is pivotally supported via the bearings 31 .
- the second bearing holes 53 b and 54 b are coaxially formed to have substantially the same inner diameter, and each of bearings 41 is internally fitted thereto so that the output shaft 40 is pivotally supported via the bearings 41 .
- the first bearing hole 54 a and the second bearing hole 54 b on the lower surface 54 are closed by cover members 541 and 542 at height (depth) positions close to openings thereof.
- the cover members 541 and 542 preferably have satisfactory thermal conductivity.
- portions having the first bearing holes 53 a and 54 a and the second bearing holes 53 b and 54 b are all integrally formed of a single material.
- the lower surface 54 of the casing 50 is formed to be gradually located downward as the lower surface 54 is oriented rearward from a front end.
- the lower surface 54 of the casing 50 has a front end portion 54 c , a middle stage portion 54 d , and a rear half portion 54 e which are located downward in this stepwise order as the lower surface 54 is oriented rearward.
- a plurality of fins 544 are erected along the forward-rearward direction in the front end portion 54 c of the lower surface 54 .
- the plurality of fins 544 guide wind of the fan 23 provided in the input shaft 20 to the second bearing hole 54 b formed in the rear half portion 54 e of the lower surface 54 .
- the first bearing hole 54 a for supporting the intermediate shaft 30 is open in the middle stage portion 54 d of the lower surface 54 .
- the second bearing hole 54 b for supporting the output shaft 40 is open in the rear half portion 54 e of the lower surface 54 .
- the rear half portion 54 e of the lower surface 54 has four leg portions 543 fixed to a base 160 (refer to FIG. 1 ) of an upper portion of the cooling tower 100 .
- a front half portion of both side surfaces 55 of the casing 50 is formed in a smooth surface shape so that a front end is smoothly connected to the front surface 51 and is gradually located to a lateral side as the front end is oriented toward the rear half portion.
- the rear half portion of the side surface 55 of the casing 50 has a plurality of (two in the present embodiment) groove portions 551 provided along the axial direction (upward-downward direction) of the output shaft 40 .
- the plurality of groove portions 551 are aligned in the forward-rearward direction, and a lower end thereof is connected to the rear half portion 54 e of the lower surface 54 of the casing 50 between the two leg portions 543 .
- the upper surface 53 of the casing 50 is smoothly connected to the front surface 51 in the front end, and is formed in a flat surface shape.
- a substantially flat plate-shaped top cover 57 is attached to the upper surface 53 of the casing 50 .
- the top cover 57 exposes the output shaft 40 from the insertion hole 57 a located above the first bearing hole 53 a , and closes the second bearing hole 53 b.
- the top cover 57 closes an oil circulation hole (ejection hole) 53 c formed on the upper surface 53 of the casing 50 .
- the oil circulation hole 53 c is formed in front of the first bearing hole 53 a , and a lubricant wound upward inside the casing 50 is ejected upward of the upper surface 53 by a splasher 24 attached to the input shaft 20 .
- the lubricant is supplied from the upper side of the upper surface 53 to the bearing 31 inside the first bearing hole 53 a , and returns to the casing 50 .
- An annular seal member 58 for sealing a gap between the top cover 57 and the output shaft 40 is provided inside the insertion hole 57 a of the top cover 57 .
- the seal member 58 is exposed to the outside of the casing 50 (top cover 57 ).
- FIG. 5 is an enlarged view of a section A in FIG. 4 , and is a view for describing the seal member 58 .
- the seal member 58 has a first member 581 externally fitted to the output shaft 40 and a second member 584 internally fitted to the top cover 57 .
- the first member 581 has a first core bar 582 which is a main body of the first member 581 and a first elastic body 583 which covers a periphery of the first core bar 582 .
- the first core bar 582 has a cylindrical portion 582 a externally fitted to the output shaft 40 and a flange portion 582 b extending outward in a radial direction of the axis of the output shaft 40 from an upper end of the cylindrical portion 582 a , and is formed in an L-shape in cross section.
- the first elastic body 583 is formed in a shape corresponding to the first core bar 582 , and covers the periphery of the first core bar 582 .
- the first elastic body 583 has a first lip portion 583 a provided in a tip of an outer peripheral portion. A tip of the first lip portion 583 a is in contact with the second member 584 .
- the second member 584 has a second core bar 585 which is the main body of the second member 584 , and a second elastic body 586 that covers the periphery of the second core bar 585 .
- the second core bar 585 has a cylindrical portion 585 a externally fitted to the insertion hole 57 a of the top cover 57 and a flange portion 585 b extending inward in the radial direction of the axis of the output shaft 40 from a lower end of the cylindrical portion 585 a , and is formed in an L-shape in cross section.
- the second core bar 585 and the first core bar 582 are combined with each other so that the cylindrical portions 582 a and 585 a face each other and the flange portions 582 b and 585 b face each other.
- the first lip portion 583 a of the first member 581 comes into contact with an inner peripheral upper end of the second core bar 585 .
- the second elastic body 586 has three second lip portions 586 a to 586 c provided on an inner peripheral portion. Out of the portions, the second lip portion 586 a extends slightly upward in an inner diameter direction from the inner peripheral portion of the flange portion 585 b of the second core bar 585 , and a tip thereof is in contact with an outer peripheral surface of the cylindrical portion 582 a of the first core bar 582 .
- the second lip portion 586 b extends slightly upward in the inner diameter direction slightly above the second lip portion 586 a , and a tip thereof is in contact with the outer peripheral surface of the cylindrical portion 582 a of the first core bar 582 .
- the second lip portion 586 c extends upward from the inner peripheral portion of the flange portion 585 b of the second core bar 585 , and a tip thereof is in contact with a lower surface of the flange portion 582 b of the first core bar 582 .
- the number and a shape of the second lip portions 586 a to 586 c are not particularly limited.
- a space between the first member 581 and the second member 584 that is, a space between the adjacent second lip portions 586 a to 586 c or a space between the second lip portion 586 c and the first lip portion 583 a is filled with a lubricant G.
- a ratio of an outer diameter (diameter) D 2 to an inner diameter (diameter) D 1 is preferably 1.6 or higher, and this ratio more preferably falls within a range of 1.8 to 2.0.
- the ratio is set in this way, in order to dispose the seal member 58 , it is not necessary to prepare a dedicated cover having a small inner diameter.
- the speed reducer 1 when power of the motor 150 is input to rotate the input shaft 20 , the speed of this motion is reduced via the gear set of the bevel pinion 22 and the bevel gear 32 , and the motion is transmitted to the intermediate shaft 30 . Thereafter, the speed of the motion is further reduced via the gear set of the intermediate gear 33 and the output gear 42 , and the motion is transmitted to the output shaft 40 . In this way, the speed-reduced power is output from the output shaft 40 to the cooling fan 140 , and the cooling fan 140 is rotationally driven.
- the gap between the output shaft 40 and the top cover 57 is sealed with the seal member 58 .
- the first member 581 is externally fitted to the output shaft 40
- the second member 584 is internally fitted to the casing 50 (top cover 57 ) so that the first member 581 and the second member 584 are relatively rotated.
- the first lip portion 583 a of the first member 581 comes into sliding contact with the second core bar 585
- the second lip portions 586 a to 586 c of the second member 584 come into sliding contact with the first core bar 582 .
- an upper side and a lower side of the seal member 58 that is, an upper side and a lower side of the casing 50 (top cover 57 ) are preferably sealed.
- the output shaft 40 does not come into sliding contact with any member.
- a sliding contact mark (abrasion mark)
- the seal member 58 disposed between the output shaft 40 and the casing 50 (top cover 57 ) has the first member 581 externally fitted to the output shaft 40 and the second member 584 internally fitted to the top cover 57 .
- the first member 581 has the first core bar 582 and the first lip portion 583 a provided on the outer periphery of the first core bar 582 .
- the second member 584 has the second core bar 585 with which the first lip portion 583 a comes into contact and the second lip portions 586 a to 586 c provided on the inner periphery of the second core bar 585 to come into contact with the first core bar 582 .
- the first lip portion 583 a of the first member 581 comes into sliding contact with the second core bar 585
- the second lip portions 586 a to 586 c of the second member 584 come into sliding contact with the first core bar 582 .
- the upper side and the lower side of the seal member 58 that is, the upper side and the lower side of the casing 50 (top cover 57 ) are preferably sealed.
- first member 581 externally fitted to the output shaft 40 and the second member 584 internally fitted to the casing 50 (top cover 57 ) are relatively rotated, and the output shaft 40 does not come into sliding contact with any member.
- the output shaft 40 does not come into sliding contact with any member.
- the space between the first member 581 and the second member 584 is filled with the lubricant.
- a gap between the output shaft 40 and the casing 50 can be more preferably sealed, and moisture can be prevented from entering the inside of the speed reducer 1 .
- the seal member according to the present invention can be widely applied to those which are disposed between the shaft and the casing to seal the gap.
- the seal member may be applied to the seal member 25 that seals the gap between the input shaft 20 and the casing 50 (shaft support member 56 ).
- the ratio of the outer diameter (diameter) D 2 to the inner diameter (diameter) D 1 is preferably 2.0 or higher, and the ratio more preferably falls within a range of 2.2 to 2.5.
- the seal member 58 is disposed between the output shaft 40 and the top cover 57 .
- the seal member 58 may be disposed between the output shaft 40 and the casing 50 .
- sealing performance may be further improved by sealing the gap between the output shaft 40 and the casing 50 (top cover 57 ) with the seal member 58 and providing a slinger member (refer to FIG. 6 ) on the outside thereof.
- a type of the cooling tower according to the present invention is not particularly limited as long as the cooling tower has the cooling fan.
- cooling tower speed reducer according to the present invention is not limited to a perpendicular type speed reducer as long as the speed reducer has an exposed shaft.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- General Details Of Gearings (AREA)
- Sealing With Elastic Sealing Lips (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
- Sealing Devices (AREA)
Abstract
There is provided a cooling tower speed reducer that reduces a speed of rotation input from an input shaft to rotationally drive a cooling fan installed inside a cooling tower. The cooling tower speed reducer includes a seal member disposed between a shaft and a casing. The seal member includes a first member externally fitted to the shaft and a second member internally fitted to the casing. The first member includes a first member main body and a first lip portion provided on an outer periphery of the first member main body. The second member includes a second member main body with which the first lip portion comes into contact and second lip portions provided on an inner periphery of the second member main body to come into contact with the first member main body.
Description
- The content of Japanese Patent Application No. 2019-235413 on the basis of which priority benefits are claimed in an accompanying application data sheet, is in its entirety incorporated herein by reference.
- Certain embodiments of the present invention relate to a cooling tower speed reducer.
- In the related art, a cooling tower speed reducer is known which drives a cooling fan of a cooling tower. In this type of speed reducers, a problem may arise in sealing performance between an externally exposed shaft (for example, an output shaft) and a casing in some cases. In particular, in a wet cooling tower that sprays water, the speed reducer is exposed to a high humidity atmosphere. Consequently, it is necessary to satisfactorily maintain the sealing performance between the shaft and the casing so that not only dust but also moisture does not enter an inside of the speed reducer.
- According to an embodiment of the present invention, there is provided a cooling tower speed reducer that reduces a speed of rotation input from an input shaft to rotationally drive a cooling fan installed inside a cooling tower.
- The cooling tower speed reducer includes a seal member disposed between a shaft and a casing.
- The seal member includes a first member externally fitted to the shaft and a second member internally fitted to the casing.
- The first member includes a first member main body and a first lip portion provided on an outer periphery of the first member main body.
- The second member includes a second member main body with which the first lip portion comes into contact, and second lip portions provided on an inner periphery of the second member main body to come into contact with the first member main body.
-
FIG. 1 is a sectional view illustrating a cooling tower to which a cooling tower speed reducer according to an embodiment of the present invention is applied. -
FIG. 2A is a perspective view when the cooling tower speed reducer according to the embodiment is viewed from an obliquely upper front side, andFIG. 2B is a perspective view when the cooling tower speed reducer is viewed from an obliquely lower front side. -
FIG. 3A is a side view of the cooling tower speed reducer according to the embodiment, andFIG. 3B is a perspective view when the cooling tower speed reducer is viewed from an obliquely lower rear side. -
FIG. 4 is a side sectional view of the cooling tower speed reducer according to the embodiment. -
FIG. 5 is an enlarged view of a section A inFIG. 4 . -
FIG. 6 is a view illustrating a seal structure between a shaft and a casing in the related art. - It is desirable to preferably seal a gap between a shaft and a casing with a simple configuration.
- According to an embodiment of the present invention, it is possible to preferably seal a gap between a shaft and a casing with a simple configuration.
- For example, as illustrated in
FIG. 6 , in some cases, a gap between a casing and a shaft is sealed with an oil seal, and a slinger member is provided in the shaft so that a gap between a seal portion and the slinger member is filled with a lubricant. In this manner, a speed reducer prevents oil from leaking out of the speed reducer or prevents external moisture from entering the speed reducer. However, according to this configuration, it is necessary to provide the slinger member. Consequently, the number of components increases, and the speed reducer has a complicated configuration. - Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.
-
FIG. 1 is a sectional view illustrating acooling tower 100 to which a cooling tower speed reducer 1 according to an embodiment of the present invention is applied. - As illustrated in the drawing, the cooling tower speed reducer (hereinafter, simply referred to as a “speed reducer”) 1 according to the present embodiment is applied to the
cooling tower 100. - The
cooling tower 100 cools cooling water used in a cryocooler for air conditioning or a process fluid for refining crude oil. In thecooling tower 100, warmed cooling water W1 introduced into atower unit 110 is sprayed onto a surface of afiller 130 by asprinkler 120, and external air A1 fetched by acooling fan 140 is blown to dropping water W2. In this manner, the water W2 is partially evaporated, the remaining water is cooled, and cooling water W3 collected in a bottom portion of thetower unit 110 is circulated to an air conditioner by a pump. - The
cooling fan 140 is provided in an upper portion of thetower unit 110, and discharges moisture evaporated in thetower unit 110 to external air above. Thecooling fan 140 is connected to amotor 150 via thespeed reducer 1. Thespeed reducer 1 reduces a speed of power of themotor 150, and outputs the power to rotationally drive thecooling fan 140. - Various types of the cooling towers are present in addition to an open type illustrated in
FIG. 1 . Thespeed reducer 1 of the present embodiment can be used for any type of the cooling towers (for driving the cooling fan). For example, thespeed reducer 1 can also be used for an air-cooled heat exchanger (air fin cooler) having a closed type, a suction ventilation type, or a force ventilation type. - Subsequently, a configuration of the
speed reducer 1 will be described. -
FIGS. 2A and 2B are perspective views when thespeed reducer 1 is viewed from an obliquely upper front side and an obliquely lower front side.FIGS. 3A and 3B are side views of thespeed reducer 1, and are perspective views when thespeed reducer 1 is viewed from an obliquely lower rear side.FIG. 4 is a side sectional view of thespeed reducer 1. - As illustrated in
FIGS. 2A to 4 , thespeed reducer 1 includes aninput shaft 20, anintermediate shaft 30, and anoutput shaft 40 which are sequentially connected to transmit power, and acasing 50 that accommodates the shafts. - The
input shaft 20 is disposed so that an axial direction is oriented in a substantially horizontal direction, and theintermediate shaft 30 and theoutput shaft 40 are disposed so that the respective axial directions are oriented in an upward-downward direction substantially perpendicular to theinput shaft 20. Theinput shaft 20, theintermediate shaft 30, and theoutput shaft 40 are pivotally supported bybearings casing 50. In addition, the respective axes of theinput shaft 20, theintermediate shaft 30, and theoutput shaft 40 are located in the mutually same plane. - In the following description, directions of the
speed reducer 1 will be defined as follows. A direction along the input shaft 20 (rightward-leftward direction on a paper surface inFIG. 4 ) will be set as a “forward-rearward direction”, a vertical direction perpendicular to the forward-rearward direction on the paper surface inFIG. 4 will be set as the “rightward-leftward direction”, and a direction along the output shaft 40 (upward-downward direction on the paper surface inFIG. 4 ) will be set as the “upward-downward direction”. In addition, in the “forward-rearward direction”, a side where theinput shaft 20 is exposed from thecasing 50 will be set as a “front side”, and a side opposite thereto will be set as a “rear side”. - A
bevel pinion 22 is formed in a rear side tip of theinput shaft 20. Thebevel pinion 22 meshes with abevel gear 32 connected to theintermediate shaft 30 to be integrally rotated. Anintermediate gear 33 is formed on an outer peripheral surface of theintermediate shaft 30. Theintermediate gear 33 meshes with anoutput gear 42 connected to theoutput shaft 40 to be integrally rotated. - A front side tip of the
input shaft 20 is exposed from thecasing 50, and a motor 150 (refer toFIG. 1 ) is connected to the tip to receive input power (rotating motion). An upper end of theoutput shaft 40 is exposed from thecasing 50, and is connected to the cooling fan 140 (refer toFIG. 1 ). - According to this configuration, a rotating motion input to the
input shaft 20 is transmitted to theoutput shaft 40 while a speed of the rotational motion is reduced via a gear set of thebevel pinion 22 and thebevel gear 32 and a gear set of theintermediate gear 33 and theoutput gear 42, and is output from theoutput shaft 40 to the coolingfan 140. Here, thebevel pinion 22, thebevel gear 32, theintermediate shaft 30, theintermediate gear 33, and theoutput gear 42 form a reduction mechanism that reduces a speed of rotation of theinput shaft 20 and transmits the rotation to theoutput shaft 40. However, a specific configuration of the reduction mechanism is not particularly limited as long as the reduction mechanism is accommodated in thecasing 50 and reduces the speed of the rotation of theinput shaft 20 to transmit the rotation to theoutput shaft 40. For example, the gear set of thebevel pinion 22 and thebevel gear 32 may be a gear set of a hypoid gear or a worm gear. - In addition, a fan (impeller) 23 is disposed in a tip of a front side portion exposed (protruded) from the
casing 50 in the input shaft 20 (omitted in the illustration inFIG. 4 ). Thefan 23 rotates in association with the rotation of theinput shaft 20, and blows wind toward thecasing 50 located behind. - The
casing 50 is an integral cast component (made of cast iron) formed in a substantially rectangular parallelepiped shape that is slightly long in the forward-rearward direction. Thecasing 50 has afront surface 51, arear surface 52, anupper surface 53, alower surface 54, and both right and left side surfaces 55 and 55. - A circular through-
hole 51 a is formed on thefront surface 51 of thecasing 50. Ashaft support member 56 that pivotally supports theinput shaft 20 via abearing 21 is attached to the through-hole 51 a. Theshaft support member 56 is formed in a substantially cylindrical shape along the forward-rearward direction, and is fixed to thecasing 50 in a state where a rear half portion is inserted into thecasing 50 from the through-hole 51 a. A front end of theshaft support member 56 has aseal member 25 that seals a gap formed with theinput shaft 20. - A through-
hole 52 a is formed on therear surface 52 of thecasing 50. The through-hole 52 a has a wide shape in the rightward-leftward direction, and is formed to have a size through which a gear member of thebevel gear 32 and theoutput gear 42 can pass. The through-hole 52 a is a hole portion for incorporating thebevel gear 32 and theoutput gear 42 into thecasing 50 when assembled. When assembled, theintermediate gear 33 and theoutput gear 42 are inserted into thecasing 50 from the through-hole 52 a, and are attached to theintermediate shaft 30 and theoutput shaft 40 inside thecasing 50. The through-hole 52 a is closed by acover member 521. - First bearing holes 53 a and 54 a for supporting the
intermediate shaft 30 and second bearing holes 53 b and 54 b for supporting theoutput shaft 40 are formed on theupper surface 53 and thelower surface 54 of thecasing 50. The first bearing holes 53 a and 54 a are coaxially formed to have substantially the same inner diameter, and each ofbearings 31 is internally fitted thereto so that theintermediate shaft 30 is pivotally supported via thebearings 31. The second bearing holes 53 b and 54 b are coaxially formed to have substantially the same inner diameter, and each ofbearings 41 is internally fitted thereto so that theoutput shaft 40 is pivotally supported via thebearings 41. Thefirst bearing hole 54 a and thesecond bearing hole 54 b on thelower surface 54 are closed bycover members cover members casing 50, portions having the first bearing holes 53 a and 54 a and the second bearing holes 53 b and 54 b are all integrally formed of a single material. - The
lower surface 54 of thecasing 50 is formed to be gradually located downward as thelower surface 54 is oriented rearward from a front end. In the present embodiment, thelower surface 54 of thecasing 50 has afront end portion 54 c, amiddle stage portion 54 d, and arear half portion 54 e which are located downward in this stepwise order as thelower surface 54 is oriented rearward. - Out of these portions, a plurality of
fins 544 are erected along the forward-rearward direction in thefront end portion 54 c of thelower surface 54. The plurality offins 544 guide wind of thefan 23 provided in theinput shaft 20 to thesecond bearing hole 54 b formed in therear half portion 54 e of thelower surface 54. - The
first bearing hole 54 a for supporting theintermediate shaft 30 is open in themiddle stage portion 54 d of thelower surface 54. - The
second bearing hole 54 b for supporting theoutput shaft 40 is open in therear half portion 54 e of thelower surface 54. In addition, therear half portion 54 e of thelower surface 54 has fourleg portions 543 fixed to a base 160 (refer toFIG. 1 ) of an upper portion of thecooling tower 100. - A front half portion of both side surfaces 55 of the
casing 50 is formed in a smooth surface shape so that a front end is smoothly connected to thefront surface 51 and is gradually located to a lateral side as the front end is oriented toward the rear half portion. - In addition, the rear half portion of the
side surface 55 of thecasing 50 has a plurality of (two in the present embodiment)groove portions 551 provided along the axial direction (upward-downward direction) of theoutput shaft 40. The plurality ofgroove portions 551 are aligned in the forward-rearward direction, and a lower end thereof is connected to therear half portion 54 e of thelower surface 54 of thecasing 50 between the twoleg portions 543. - The
upper surface 53 of thecasing 50 is smoothly connected to thefront surface 51 in the front end, and is formed in a flat surface shape. - A substantially flat plate-shaped
top cover 57 is attached to theupper surface 53 of thecasing 50. Thetop cover 57 exposes theoutput shaft 40 from theinsertion hole 57 a located above thefirst bearing hole 53 a, and closes thesecond bearing hole 53 b. - In addition, the
top cover 57 closes an oil circulation hole (ejection hole) 53 c formed on theupper surface 53 of thecasing 50. Theoil circulation hole 53 c is formed in front of thefirst bearing hole 53 a, and a lubricant wound upward inside thecasing 50 is ejected upward of theupper surface 53 by asplasher 24 attached to theinput shaft 20. The lubricant is supplied from the upper side of theupper surface 53 to thebearing 31 inside thefirst bearing hole 53 a, and returns to thecasing 50. - An
annular seal member 58 for sealing a gap between thetop cover 57 and theoutput shaft 40 is provided inside theinsertion hole 57 a of thetop cover 57. Theseal member 58 is exposed to the outside of the casing 50 (top cover 57). -
FIG. 5 is an enlarged view of a section A inFIG. 4 , and is a view for describing theseal member 58. - As illustrated in the drawing, the
seal member 58 has afirst member 581 externally fitted to theoutput shaft 40 and asecond member 584 internally fitted to thetop cover 57. - The
first member 581 has afirst core bar 582 which is a main body of thefirst member 581 and a firstelastic body 583 which covers a periphery of thefirst core bar 582. - The
first core bar 582 has acylindrical portion 582 a externally fitted to theoutput shaft 40 and aflange portion 582 b extending outward in a radial direction of the axis of theoutput shaft 40 from an upper end of thecylindrical portion 582 a, and is formed in an L-shape in cross section. - The first
elastic body 583 is formed in a shape corresponding to thefirst core bar 582, and covers the periphery of thefirst core bar 582. In addition, the firstelastic body 583 has afirst lip portion 583 a provided in a tip of an outer peripheral portion. A tip of thefirst lip portion 583 a is in contact with thesecond member 584. - The
second member 584 has asecond core bar 585 which is the main body of thesecond member 584, and a secondelastic body 586 that covers the periphery of thesecond core bar 585. - The
second core bar 585 has acylindrical portion 585 a externally fitted to theinsertion hole 57 a of thetop cover 57 and aflange portion 585 b extending inward in the radial direction of the axis of theoutput shaft 40 from a lower end of thecylindrical portion 585 a, and is formed in an L-shape in cross section. Thesecond core bar 585 and thefirst core bar 582 are combined with each other so that thecylindrical portions flange portions first lip portion 583 a of thefirst member 581 comes into contact with an inner peripheral upper end of thesecond core bar 585. - The second
elastic body 586 has threesecond lip portions 586 a to 586 c provided on an inner peripheral portion. Out of the portions, thesecond lip portion 586 a extends slightly upward in an inner diameter direction from the inner peripheral portion of theflange portion 585 b of thesecond core bar 585, and a tip thereof is in contact with an outer peripheral surface of thecylindrical portion 582 a of thefirst core bar 582. Thesecond lip portion 586 b extends slightly upward in the inner diameter direction slightly above thesecond lip portion 586 a, and a tip thereof is in contact with the outer peripheral surface of thecylindrical portion 582 a of thefirst core bar 582. Thesecond lip portion 586 c extends upward from the inner peripheral portion of theflange portion 585 b of thesecond core bar 585, and a tip thereof is in contact with a lower surface of theflange portion 582 b of thefirst core bar 582. The number and a shape of thesecond lip portions 586 a to 586 c are not particularly limited. - A space between the
first member 581 and thesecond member 584, that is, a space between the adjacentsecond lip portions 586 a to 586 c or a space between thesecond lip portion 586 c and thefirst lip portion 583 a is filled with a lubricant G. - In addition, in the
seal member 58, a ratio of an outer diameter (diameter) D2 to an inner diameter (diameter) D1 is preferably 1.6 or higher, and this ratio more preferably falls within a range of 1.8 to 2.0. When the ratio is set in this way, in order to dispose theseal member 58, it is not necessary to prepare a dedicated cover having a small inner diameter. - Subsequently, an operation of the
speed reducer 1 will be described. - In the
speed reducer 1, when power of themotor 150 is input to rotate theinput shaft 20, the speed of this motion is reduced via the gear set of thebevel pinion 22 and thebevel gear 32, and the motion is transmitted to theintermediate shaft 30. Thereafter, the speed of the motion is further reduced via the gear set of theintermediate gear 33 and theoutput gear 42, and the motion is transmitted to theoutput shaft 40. In this way, the speed-reduced power is output from theoutput shaft 40 to the coolingfan 140, and the coolingfan 140 is rotationally driven. - In this case, in the
speed reducer 1, as illustrated inFIG. 5 , the gap between theoutput shaft 40 and thetop cover 57 is sealed with theseal member 58. - In the
seal member 58, thefirst member 581 is externally fitted to theoutput shaft 40, and thesecond member 584 is internally fitted to the casing 50 (top cover 57) so that thefirst member 581 and thesecond member 584 are relatively rotated. Then, thefirst lip portion 583 a of thefirst member 581 comes into sliding contact with thesecond core bar 585, and thesecond lip portions 586 a to 586 c of thesecond member 584 come into sliding contact with thefirst core bar 582. In this manner, an upper side and a lower side of theseal member 58, that is, an upper side and a lower side of the casing 50 (top cover 57) are preferably sealed. - In addition, in this case, the
output shaft 40 does not come into sliding contact with any member. In this manner, for example, unlike a case where a lip portion of a seal ring is directly brought into sliding contact with theoutput shaft 40, it is possible to prevent a sliding contact mark (abrasion mark) from being formed in theoutput shaft 40. - As described above, according to the present embodiment, the
seal member 58 disposed between theoutput shaft 40 and the casing 50 (top cover 57) has thefirst member 581 externally fitted to theoutput shaft 40 and thesecond member 584 internally fitted to thetop cover 57. Thefirst member 581 has thefirst core bar 582 and thefirst lip portion 583 a provided on the outer periphery of thefirst core bar 582. Thesecond member 584 has thesecond core bar 585 with which thefirst lip portion 583 a comes into contact and thesecond lip portions 586 a to 586 c provided on the inner periphery of thesecond core bar 585 to come into contact with thefirst core bar 582. - In this manner, in the
seal member 58, thefirst lip portion 583 a of thefirst member 581 comes into sliding contact with thesecond core bar 585, and thesecond lip portions 586 a to 586 c of thesecond member 584 come into sliding contact with thefirst core bar 582. In this manner, the upper side and the lower side of theseal member 58, that is, the upper side and the lower side of the casing 50 (top cover 57) are preferably sealed. - Therefore, unlike the related art which requires a slinger member, it is possible to seal a gap between the
output shaft 40 and thecasing 50 with a simple configuration. - Furthermore, the
first member 581 externally fitted to theoutput shaft 40 and thesecond member 584 internally fitted to the casing 50 (top cover 57) are relatively rotated, and theoutput shaft 40 does not come into sliding contact with any member. In this manner, for example, unlike a case where the lip portion of the seal ring is directly brought into sliding contact with theoutput shaft 40, it is possible to prevent a sliding contact mark from being formed in theoutput shaft 40. - In addition, according to the present embodiment, in the
seal member 58, the space between thefirst member 581 and thesecond member 584 is filled with the lubricant. - In this manner, a gap between the
output shaft 40 and thecasing 50 can be more preferably sealed, and moisture can be prevented from entering the inside of thespeed reducer 1. - Hitherto, the embodiment of the present invention has been described. However, the present invention is not limited to the above-described embodiment.
- For example, in the above-described embodiment, a case has been described where a structure of the seal member according to the present invention is applied to the
seal member 58 that seals the gap between theoutput shaft 40 and the casing 50 (top cover 57). However, the seal member according to the present invention can be widely applied to those which are disposed between the shaft and the casing to seal the gap. For example, the seal member may be applied to theseal member 25 that seals the gap between theinput shaft 20 and the casing 50 (shaft support member 56). Here, when applied to theseal member 25, the ratio of the outer diameter (diameter) D2 to the inner diameter (diameter) D1 is preferably 2.0 or higher, and the ratio more preferably falls within a range of 2.2 to 2.5. When the ratio is set in this way, in order to dispose theseal member 25, it is not necessary to prepare a dedicated cover having a small inner diameter. - In addition, in the above-described embodiment, the
seal member 58 is disposed between theoutput shaft 40 and thetop cover 57. However, theseal member 58 may be disposed between theoutput shaft 40 and thecasing 50. - In addition, sealing performance may be further improved by sealing the gap between the
output shaft 40 and the casing 50 (top cover 57) with theseal member 58 and providing a slinger member (refer toFIG. 6 ) on the outside thereof. - In addition, a type of the cooling tower according to the present invention is not particularly limited as long as the cooling tower has the cooling fan.
- In addition, the cooling tower speed reducer according to the present invention is not limited to a perpendicular type speed reducer as long as the speed reducer has an exposed shaft.
- In addition, details in the above-described embodiment can be appropriately modified within the scope not departing from the concept of the invention.
- It should be understood that the invention is not limited to the above-described embodiment, but may be modified into various forms on the basis of the spirit of the invention. Additionally, the modifications are included in the scope of the invention.
Claims (7)
1. A cooling tower speed reducer that reduces a speed of rotation input from an input shaft to rotationally drive a cooling fan installed inside a cooling tower, comprising:
a seal member disposed between a shaft and a casing,
wherein the seal member includes a first member externally fitted to the shaft and a second member internally fitted to the casing,
the first member includes a first member main body and a first lip portion provided on an outer periphery of the first member main body, and
the second member includes a second member main body with which the first lip portion comes into contact and second lip portions provided on an inner periphery of the second member main body to come into contact with the first member main body.
2. The cooling tower speed reducer according to claim 1 ,
wherein the seal member is exposed to an outside of the casing.
3. The cooling tower speed reducer according to claim 1 ,
wherein in the seal member, a space between the first member and the second member is filled with a lubricant.
4. The cooling tower speed reducer according to claim 1 ,
wherein the casing includes an ejection hole for the lubricant and a cover that closes the ejection hole, and
the seal member is disposed between the shaft and the cover.
5. The cooling tower speed reducer according to claim 1 ,
wherein the shaft is an output shaft that outputs the speed-reduced rotation.
6. The cooling tower speed reducer according to claim 5 ,
wherein in the seal member, a ratio of an outer diameter to an inner diameter is 1.6 or higher.
7. The cooling tower speed reducer according to claim 1 ,
wherein the shaft is the input shaft, and
in the seal member disposed between the input shaft and the casing, a ratio of an outer diameter to an inner diameter is 2.0 or higher.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2019235413A JP2021102997A (en) | 2019-12-26 | 2019-12-26 | Speed reducer for cooling tower |
JP2019-235413 | 2019-12-26 |
Publications (1)
Publication Number | Publication Date |
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US20210199381A1 true US20210199381A1 (en) | 2021-07-01 |
Family
ID=73856511
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US17/132,729 Abandoned US20210199381A1 (en) | 2019-12-26 | 2020-12-23 | Cooling tower speed reducer |
Country Status (4)
Country | Link |
---|---|
US (1) | US20210199381A1 (en) |
EP (1) | EP3842672A1 (en) |
JP (1) | JP2021102997A (en) |
CN (1) | CN113048194A (en) |
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